Capstan for wire drawing machines



Sept. l1, 1934. R, c. YoUsEY CAPSTAN FOR WIRE DRAWING MACHINES INVENTOR mz/mb mmf sept, 11, 1934.

2 Sheets-Sheet 2 v Filed May 24, 1952 INVENTOR ATTORNEY'.

Patented Sept. 11, 1934 rentes `CAPS'IAN 'FOR WIRE Reuben C. You

DRAWING MACHINES sey, Rome, N. Y.

Application May 24, 1932, Serial N0. 613,209

3 Claims.

My invention relates to a capstan for a wire drawing machine and I declare the following to be a full, clear, concise and exact description thereof suliicient to enable anyone skilled inthe art to which it appertains to make and use the same, reference being had to the accompanying drawings in which likereference characters refer to like parts throughout the specification.

The object of the invention is to provide a capstan ior wire drawing machines in which the `wire is being reduced progressively bydrawing it through a series of dies having apertures that progressively diminish in size. 4It will be understood in the -process of drawing wire .into longer lengths, that none of the metal is lost or removed. The diameter, however, is reduced and the length is increased ina direct ratio or proportion with the decreased diameter.

In drawing wire, however, one oi vthe problems to be met is in compensating for the diiier'ence in length of the wire from -the time it enters Vthe machine to the time it leaves the machine. As the wire passes through each successive die, it will be reduced in diameter and proportionately lengthened. The aggregate or resultant total lengthening ofthe wire, effected by all of the dies must be compensated for on the-takedlp roll either by a Variable speed yin the roll or .by allowing the wire toslip. d

This -latter or slipping meansof compensating is harmful to the roll, for the reason that .it causesgrooves therein and makes it necessary to renew the roll periodically. AvIt also causes a loss of power or eiiiciency of the machine due to theexcessive friction'caused by the Wire :slipping cn the surface of the takeup roll which loss must'be made .up by additional power.

The invention will be understood `by referring to the drawings, in which,

Fig. 1 is va central vertical sectionof vthe device i showing parts infull.

Fig. 2 is a sectional view taken on the line 2,2oflig.3.V

Fig. 3 lis a side elevation of Aone of the sheaves employed. Y

Fig. 4 is aplane view-of certainretaining members employed showing other parts kin section.

Fig. 5 is ya ydetail View showing a vperspective oi one oi the retaining members which are used vin pairs.

Fig.'6 is aperspective view of vthe wire drawing machine shown in relation to'other related parts of a wire drawing machine, parts being omitted.

Referring more particularly to the drawings, the device embodies a master shaft l which is revolved by means of any well-known source of power. There is keyed or otherwise mounted to turn with shaft l a gear pinion 2 which meshes with gear 3 of much larger diameter. Gear 3 is keyed to turn with auxiliary shaft 4 which is sup ported in bearing 5 carried by frame 6. There is also mounted on auxiliary shaft 4 a gear pinion 'l which is in mesh with a ge r of larger diameter 8. Gear S has a flange portion l0 and is mounted to turn freely on tubular member ll. Tubular Amember l1 is clamped in bearing 12 of frame 6. A washer or sealing member 13 is bolted at l-i 'to frame 6. A bronze bushing l5 is employed between the bearing surfaces oi gear 8 and tubular member 11. Shaft l is disposed through the center of tubular member l1 though not in ecntact therewith and turns independently thereof. Shaft l at one end turns in bushing 16 mounted in bearing member 12. At the other end, shaft l is tapered at 18 and has a fixed bearing in end 75 member 19 to which it is keyed at 20 whereby to turn therewith. End member 19 is bolted at 2l to sheave 36 whereby said sheave 36 will turn with end member 19.

There are mounted to turn freely upon tubular member .11, intermediate sheaves 22 to 36 inclusive.- All of the sheaves 22 to 36 are made substantially alike and all turn in the same direction. Each has an annular groove 37 in its periphery for holding the coils of wire 38 wound thereon and a circumferential shoulder 39 to overlap the peripheral edge 40 of the next adjacent sheave on its right, whereby to prevent wire 38 from slipping between the sheaves. Furthermore, the side portion li1 of each of the sheaves 22 to 36 is reduced and has formed in said reduced parts, one or more recesses, 42, 4t2-wn., preferably four of recesses 42 and four of recesses 42-A. In end sheaves 22 and 36, the recesses corresponding to 42 are countersunk portions to provide clearance for the projecting portions of adjacent parts of beveled pinions 43 hereinafter described. In each of these recesses Ll2 i2-42A is disposed in a loose manner, a bevel pinion 43 which is free to revolve and is adapted to mesh with a circumferential gear rack 45 formed on both sides of each of sheaves 23 to 35 inclusive, but on one side only of end sheaves 23 and 36. Furthermore, in sheaves 22, 23, 25, 27, 29, 31, 33, 35' and 36, recesses l2 are disposed on a given circumference that is a little farther from the center of said sheaves than the like recesses Llf2-A in sheaves 24, 26, 28, 30, 32 and 34 where they are formed on a given circumference a little jnearer the center of said sheaves. This isdone 11.0

beveled pinions 43 and 43--A will be disposed in such manner that they alternate with reference to their relative distances from the center of said sheaves 23 to 35 inclusive and similarly gear racks 45 and 45--A inclusive will correspondingly alternate with reference to the center of sheaves 22 to 36 inclusive.

Each of the bevel pinions 43, i3-A respectively is held whereby to turn freely in a recess 42 by open-sided retaining members 46, 46 used in pairs and bolted to opposite sides of the web 41 of each sheave 23 to 35, and in the other half or in sheaves 24, 26, 23, 30, 32 and 34 at a lesser distance or radius from the center. When assembled, sheaves 22 to 36 inclusive will be so disposed that recesses 42 formed at longer and shorter distances from the center of each sheave lwill alternate with each other, whereby bevel pinions 43 will not interfere with each other.

Sheave 22 is bolted at 56 to the hanged part 10 of gear 8, whereby said sheave 22 will turn freely upon tubular member 11 with the velocity of gear 8, whereas sheave 36 is bolted to the end member 19, which is keyed at 51 to turn with master` shaft 1. A nut 52 is screw mounted tothe tapered end 18 of shaft 1 whereby to hold end member 10 to the end of shaft 1. It is enclosed by cover portion 53 bolted at 54 to end member 19.

It will be observed, therefore, that sheave 22 will turn with the slower velocity of gear 3 and sheave 36 will turn with the faster velocity of gear pinion 2.

The intermediate sheaves 23 to 35 will rotate in progressively increasing velocities which are fractions of the dierential between the velocity of the sheave 22 and that oi sheave 36.

To be more specific, let us assume that sheave 24 is the equivalent of sheave 35, or as being fastened like sheave 36 to turn with shaft 1, or that sheaves 22, 23 and 24 are the only ones in the machine. This being so, sheave 22 will turn with the slower velocity of gear 8 which is sufficient to take up the elongation oi the wire 38 after being pulled through the nrst die 61 and sheave 24 will turn with the faster velocity of shaft 1, sucient to talee up the elongation of the iinished wire 38, after it has passed through the last die 75. Sheave 23 however being disposed between sheaves 22 and 24 and free to turn independently on hollow shaft 11, will be governed in its velocity of rotation by the rotary motion imparted to it from adjacent sheaves 22 and 24. This rotary motion will be effected through the medium of four bevel pinions 43, located in recesses 42 of sheave 23 which make contact with corresponding gear racks 45, 45a formed on the respective near faces of sheaves 22 and 24.

In the case above mentioned, it will be observed that the slower moving sheave 22 effects a drag upon sheave 23 by causing bevel pinions 43 to rotate slower on their own axis than they otherwise would if in mesh only with faster moving gear rack 45 of the sheave 24. This drag effects a torque on the four beveled pinions 43 in sheave 23 which will cause a planetary rotation of pinions 43, whereby to turn said sheave 23 in the same direction as that of sheaves 22 and 24 about hollow shaft 11 as an axis.

The speed of revolution thus imparted to sheave 23 will be imparted by said sheave to the next sheave 24 on its left through its gear rack 45-A. The fact that gear rack 45-A is nearer the center than the locations of beveled pinion 43 will not change the speed between that which sheave 23 receives and that which it imparts for all parts of sheave, 23 rotate about hollow shaft 11 as an axis in the same period of time, although they may describe larger circles or orbits in so doing.

Describing now the next step in this progressive increase of speeds of revolution of the sheaves 22 to 36 inclusive, sheave 23 will impart its increased revolution to the next sheave 24 on its left through its gear rack 45-A which is in mesh with the four beveled pinions 43-A of said sheave 24. Said beveled pinions 43-A., however, are in mesh with the gear rack 45--A of sheave 25 which is rotating with the velocity of sheave 36 as reduced by intermediate sheaves 26 to 35 inclusive, so that here, too, the faster velocity of revolution of sheave 25 and the slower velocity of revolution of sheave 23 will set up a torque or drag on the four beveled pinions i3-A in sheave 24, that will cause sheave 24 to rotate with a velocity that will absorb one-half of the differential of that between sheaves 23 and 36.

Likewise, sheave 24 will impart its velocity by means of its gear rack 45 through the four pinions 43 in sheave 25 and so on until we come to sheave 36 which is rotating with shaft l at the fastest velocity or that suflicient to take off the slack caused in wire 38 as it passes through the last die '75.

It will be observed that the two sets of beveled pinions 43 and 43-A and of gear racks 45 and 45-14 are necessary. In other words, each of the intermediate sheaves 23 to 35 must have a set kof beveled pinions and gear racks on its opposite sides in order that each sheave may receive as well as impart motion. Otherwise if each of said sheaves 23 to 35 had one set of beveled pinions only and no gear racks, sheave 22 would impart its rotation to beveled pinions 43 of the next adjacent sheave 23 on its left, which sheave 23 would tend to rotate to a small degree on hollow shaft 11 as an axis. Likewise, sheave 36 would impart its rotation to the beveled pinions 43 in the next adjacent sheave 35 on its right which sheave 35 would tend to rotate to a small degree on hollow shaft 11 as an axis, while all the other intermediate sheaves 25 to 35 in between would idle.

The rotation of sheaves 22 to 36 inclusive in the same direction on hollow shaft 11 will be calculated at different speeds suflicient to take up 27% elongation of wire 38 effected at each of the several dies 61 to 75 inclusive. A

Again assuming sheaves 22, 23 and 24 are the only ones in the machine; that sheave 22 is rotating at a velocity of 25 revolutions per minute; that sheave 24 is rotating at a velocity of 39.69 revolutions per minute, the intermediate sheave 23 will revolve at a speed of 32.345 revolutions per minute. It will be observed that sheave 23 rotates 26% faster than sheave 22; that sheave 24 rotates 26% faster than sheave 23 or that sheave 23 absorbs one-half the differential in speeds between sheave 22 and 24, whereby we derive the algebraic formula for ascertaining the speed of revolutions of any one of the sheaves in the series.

R. P. M. (1.26)n

In this formula R. P. M. represents the number of revolutions per minute allotted to sheave 23 which in the present instance is 25, (1.26) represents the effective percentage of increase of each of the successive sheaves. The desired percentage is 27%, 1% being deducted for inaccuracies in the dies. The exponent n represents one ess than the number of sheaves in the series. Appiying the formula to the just above mentioned iigures, we derived the following:

Likewise the velocity of any one of the sheaves can be determined by applying the above algebraic formula.

The ratio of increase in velocity between sheaves 22 and 36 will be determined by the number of intermediate sheaves employed. If there are fifteen sheaves, as in the instant case, each sheave will turn with an increasing velocity or an equal or proportionate part of the difference in velocity between the two end sheaves 22 and 36, whereby each sheave next on the right will increase velocity at a constant ratio. This constant ratio will be determined by the difference in velocity of the two end sheaves 22 and 36 as stated above, that is in the instant case, oneiifteenth faster than the next sheave on its right.

Furthermore, the number of sheaves employed will be governed by the total number of dies used in the series oi reductions required to take up the given amount of increase in length of wire desired, whereby the wire 38 will be wound in regular uniform manner upon the successive sheaves without any undue slipping.

In operation wire 38 is drawn through a plurality of dies by passing it through the iirst die, then winding it one or more times around the long pulling roll or capstan then back to one of the idle rolls and onto the next adjacent dic `lthrough which it passes and is further reduced in diameter and extended in length. The series of operations is repeated until the predetermined number of reductions in diameter and length of wire have been effected. This method is known as a continuous drawing.

More specifically, wire 38 to be drawn is projected through an aperture in a die 61 and then given a number of turns around sheave 22 ano thereafter around an idle roller 62, then projected through another die 61 which further reduces the diameter of wire 38 and further increases its length. This process will be repeated until wire 38 has passed through each of the successive dies 61 and around each of the successive sheaves 22 to 36 inclusive. At the latter location wire 38 will have been reduced to the desired diameter.

The open aperture formed in retaining member 46 serves to lighten the member. The aperture is made in forming the member.

Having thus described my invention what I claim as new and desire to secure by Letters Patent is as follows:

l. In a capstan for wire drawing machine, composed of a plurality of sheaves mounted on a common support, circumferential gear racks formed on each of said sheaves and gears carried by said sheaves, whereby to mesh with said racks, means for turning one of said sheaves at a given velocity, other means turning another one of said sheaves at a higher velocity and said gear racks and gears adapted to distribute the dierential velocity among said sheaves, whereby to wind a Wire thereon in a uniform manner.

2. In a capstan for wire drawing machine, a plurality of sheaves mounted on a common support, means loosely mounted in said sheaves for interconnecting said sheaves, whereby to compel them to rotate in the same direction, means for rotating one of said sheaves to a given velocity, other means for rotating another one of said sheaves at a different velocity, and said means mounted in said sheaves adapted to distribute the diierence in velocity in a progressive manner to said sheaves.

3. In a capstan for wire drawing machine, a pluralityiof sheaves mounted on a common support, one of said sheaves turning at a predetermined velocity, another one of said sheaves turning at a predetermined higher velocity, pinions loosely mounted in certain of said sheaves, gear racks formed on said sheaves and said gear racks meshing with said pinions, whereby to turn said sheaves in a planetary manner to distribute the diierential in speed among said sheaves.

REUBEN C. YOUSEY. 

